Double-disk, spring-biased mechanical seal assembly

ABSTRACT

A mechanical seal arrangement for use in association with a pump casing structure and a drive shaft for driving a pump impeller which is housed in the pump casing structure. The mechanical seal arrangement has a rotatable seal ring with a seal face mountable concentrically on the drive shaft for rotation with the drive shaft. A non-rotatable seal ring is provided having a seal face mounted in axial alignment with the rotatable seal ring assembly. Biasing means are provided for urging the rotatable and non-rotatable seal rings axially towards each other for effecting sealing engagement of the seal faces of the respective seal rings. The biasing means has at least two disk spring elements spaced apart and encapsulated in an elastomeric body, with the biasing means being located in use in tensioned state between either one of the seal rings and the pump casing structure.

Mechanical seals for use in slurry pumps have in the past mainlycomprised stuffing-box type seals. This is so because conventionalmechanical seals, i.e. seals comprising a non-rotating seal ring mountedto the pump casing and a rotatable seal ring mounted concentrically onthe drive shaft of the pump are very vulnerable to the highly abrasiveand sometimes corrosive environment within the pump casing of a slurrypump, which abrasive or corrosive environment can join the closeclearances and dynamic gasketry of their mechanisms. Another shortcomingof conventional types of mechanical seals for use in slurry pumps istheir inability to operate effectively at elevated internal pumppressures, and are consequently restricted to use in relative lowpressure centrifugal slurry pumps.

Some progress has however been made in recent times to adapt theconventional types of mechanical seals to make them suitable for use inslurry pumps. The most significant advancement in mechanical seal designfor slurry pumps manifested itself in a feature which serves to balancethe mechanical biassing force which urges the two sealing faces togetherwith the forces which result from the hydraulic pressure prevailinginside the pump casing when the pump is operational.

In this way, sealing arrangements have been adapted to operateeffectively at much higher pressures. The above problem has in the pastbeen overcome by quantifying the hydraulic force vectors normallyprevailing in an operative slurry pump and designing a biassing means,typically by making use of a disk spring arrangement which is adapted toexert a pre-determined net closing force on the seal faces when the pumpis operational which is commensurate with the proper functioning of theseal.

The design improvements described above have led to marked improvementsin sealing capability and operating life of mechanical seals for use inslurry pumps but the arrangements nevertheless suffer from certaindisadvantages.

Firstly, in all of the known arrangements, a single disk spring isemployed to urge the sealing faces together. This is usually done bymounting the disk spring either directly or indirectly on the driveshaft of the pump with the rotating seal ring located against it so thatthe rotating seal ring is urged towards the non-rotating seal ring bymeans of the disk spring. This arrangement has the disadvantage that thebiassing means rotates with rotating seal ring causing undesireableeffects due to centrifugal forces exerted on the biassing means.

Furthermore, the disk spring arrangement typically serves as a drive forthe rotating seal face which causes additional forces to be applied onthe disk spring and which consequently necessitates the provision ofstronger and hence more expensive biassing means designs.

Another disadvantage of the above arrangements lies in the inadequateflexibility characteristics of a single disk spring arrangement used asbiassing means for a mechanical seal. This factor becomes very importantwhen the seals are to be used in slurry pumps and particularly slurrypumps for the mining industry. Slurry pumps for the mining industry areusually relatively crude machines due to the harsh environment in whichthey are required to operate. This often has the result that the driveshaft is misaligned to some extent with reference to the pump casing. Ifone considers that the rotating seal ring is mounted to the drive shaftand the non-rotating seal ring is mounted to the pump casing then it isobvious that a substantial degree of flexibility in the biassing meansis essential in order to retain the sealing faces of the sealing ringsin permanent sealing engagement with each other. In this regard, it hasbeen found that a single disk spring arrangement is often inadequatelyflexible to accomodate the sometimes considerable variances inconcentricity and squareness which prevails between the respective sealrings during each cycle of rotation. In the past, this has been overcomeby expensive replacement or re-alignment modifications to the pumpstructure, but this is often not viable within the environment of a busymining operation.

Furthermore, solid build-up in the pump casing when the pump has beeninoperative for a period of time usually causes severe flexure orwhipping of the drive shaft during start-up. This whipping action alsohas the effect of taking the seal rings out of concentricity andconsequently the biassing means needs to be flexible enough toaccomodate the flexure and to retain the seal faces in sealingengagement with each other during start-up.

It is accordingly an object of the present invention to provide anarrangement which applicant believes will overcome or at least minimizethe problems and disadvantages of the known arrangements.

According to the invention, a mechanical seal arrangement for use inassociation with a pump casing structure and a drive shaft for driving apump impeller which is housed in the pump casing structure comprises:

a rotatable seal ring having a seal face mountable concentrically on thedrive shaft for rotation with the drive shaft;

a non-rotatable seal ring having a seal face mountable in axialalignment with the rotatable seal ring assembly; and

biassing means for urging the rotatable and non-rotatable seal ringsaxially towards each other for effecting sealing engagement of the sealfaces of the respective seal rings:

the arrangement being characterized therein that the biassing meanscomprises at least two disk spring elements spaced apart andencapsulated in an elastomeric body, the biassing means being locatablein use in a tensioned state between either one of the seal rings and thepump casing structure.

Preferably the biassing means is locatable in use in a tensioned statebetween the non-rotatable seal ring and the pump casing structure.

Preferably also two disk spring elements are encapsulated within theelastomeric body in back-to-back or series relationship.

In this specification and in the appended claims, the term "disk springelement" refers to mechanical spring in the form of a washer which isgenerally in the shape of a truncated cone, with both the base and thetruncated ends of the core being open, and the term "seriesrelationship" in respect of the disk spring elements means that the diskspring elements are arranged with their respective truncated endsextending towards each other.

The encapsulated disk spring elements are preferably mounted on asupport ring.

Preferably also, the disk spring elements are retained spaced from eachother within the elastomeric body by means of a pressure ring which islocated on the support ring between the disk spring elements at theirinner diameter regions.

The disk spring elements preferably comprise Belleville washers.

With the above arrangement therefore, the biassing means isnon-rotational and urges the non-rotatable seal ring axially towards therotatable seal ring. Furthermore, the elastomeric outer surface of thebiassing means provides an effective secondary seal against leakage offluids at the location where it abuts against the pump casing structureand at the location where it abuts against the non-rotatable seal ring.

Because use is made of two disk spring elements and rubber cushioning,the overall flexibility of the biassing means is greatly increased withthe result that the biassing means is able to compensate for much moresevere shaft vibrations, misalignments and flexures during start-up ofthe pump.

The support ring may feature at its ends radially extending abutmentsteps against which the inner diameters of the encapsulated disk springelements abut, thereby retaining the biassing means on the support ring.

An end ring may in use be located between at least one of the abutmentsteps and the inner diameter of one of the encapsulated disk springelements.

Alternatively, end rings may be shrink fitted to the ends of the supportring against which the inner diameters of the encapsulated disk springelements abut, thereby retaining the biassing means on the support ring.

An adhesive may furthermore be applied to the end rings and/or thesupport ring to enchance the bonding between the end rings and thetubular support ring.

In one form of the invention the non-rotatable seal ring is bondeddirectly to the elastomeric body of the biassing means and the rotatableseal ring is bonded directly to a shaft sleeve which is fitted over thedrive shaft.

The non-rotatable seal ring assembly preferably comprises a firstcarrier ring with a non-rotatable seal ring mounted thereon, and thepump casing structure preferably includes a pump casing and a cover ringwhich is mountable to the pump casing, the arrangement beingcharacterized therein that in use, the biasssing means is located in atensioned state between the first carrier ring and the cover ring.

The cover ring is preferably adjustable relative to the pump casing foradjusting the biassing force of the biassing means.

The rotatable seal ring assembly preferably comprises a a second carrierring with a rotatable seal ring mounted thereon, the second carrier ringbeing mounted to a shaft sleeve which is fitted over the drive shaft.

Preferably also, an annular space is defined between the inner diameterof the cover ring and the outer diameter of the shaft sleeve, a settingcollar being locatable in the annular space for locating the cover ringconcentrically relative to the drive shaft.

The setting collar may be removably attachable to the shaft sleeve.

In a preferred form of the invention, the pump casing further includesan adaptor ring; the arrangement being characterised therein that theshaft sleeve, the second carrier ring with the rotatable seal ring, thefirst carrier ring with the non-rotatable seal ring, the cover ring, theadaptor ring and the setting collar are all removable from the driveshaft as a unit in cartridge form.

This invention will now be described in detail with reference to theaccompanying drawings in which:

FIG. 1 is a sectioned side view of a biassing means forming part of theinvention;

FIG. 2 is a quarter section of one embodiment of a mechanical sealassembly according to the invention including the biassing means of FIG.1; and

FIG. 3 is a quarter section of an alternative embodiment of a mechanicalseal assembly according to the invention, including the biasing means ofFIG. 1.

FIG. 1, biassing means 10 comprises two Belville washer type disk springelements 11 arranged in series relationship as shown and encapsulated inan elastomeric body 12. The encapsulated disk spring elements 11 aremounted on a support ring 13, which is generally tubular in shape.

Support ring 13 features an abutment step 13.1 at its one end againstwhich the inner diameter of the one disk spring elements 11 abuts inuse. At the opposite end of support ring 13, a shallower abutment step13.2 is provided which serves to locate an end ring 14. The innerdiameter of the other disk spring element abuts against end ring 14which is shrink fitted onto support ring 13 and held in position byabutment step 13.2 as shown. An adhesive or contact cement (not shown)may be applied to the support ring 13 and/or end ring 14 to enhancebonding. This arrangement ultimately serves to retain the encapsulateddisk spring elements 11 securely on support ring 13.

A pivot formation 15, which forms part of support ring 13 as shown, islocated between the two disk spring elements 11 to provide a pivotsupport for the elements 11 when they are tensioned and/or flexing. Inuse, the elastomeric body 12 is bonded by way of suitable cement (notshown) to most of the surface area of the disk spring elements 11. Thereis however no bonding between the outer surface of the pivot formation15 and the elastomer in contact therewith and neither between the innerlower regions of the disk spring elements 11 and the elastomer incontact therewith.

The reason for this is to allow the elastomer to extrude unrestricted inthe region of the pressure ring 15 between the disk spring elements 11when the biassing means 10 is in a tensioned state. This arrangementaccordingly provides for a higher degree of axial travel of the elements11 relative to each other during normal operation and reduces theoverall load transmitted by the biassing means 10 to a more manageablelevel.

The outer surface configuration of the elastomeric body 12 may be variedto provide suitable hydraulic balancing surfaces on the biassing means10. This may be done by radially enlarging or reducing or varying theshape of the annular recess 16 between the outwardly extending diskspring elements 11.

In FIG. 2, a mechanical seal 20 is used in association with pump casingstructure 20.1 which includes a pump casing 21 and a drive shaft 22which drives an impeller 23 housed within casing 21.

Seal 20 generally comprises a rotatable seal ring 24 having a seal face25 and a non-rotatable seal ring 26 having seal face 27.

Rotatable seal ring 24 is mounted in a rotatable carrier ring 28 andnon-rotatable seal ring 26 is similarly mounted in a non-rotatablecarrier ring 29. The seal rings 24 and 26 may be mounted in theirrespective carrier rings my means of conventional shrink-fit orpress-fit methods to provide drive transmission to the respective sealrings. Alternatively, they may be loose mounted and driven by drive pins(not shown). They may also be mounted by means of glue or cement (notshown).

A shaft sleeve 30 is provided over drive shaft 22. Shaft sleeve 30features a radially outwardly extending flange 30.1 and rotatablecarrier ring 28 is mounted to flange 30.1 by means of a plurality ofdrive pins 31 and complementary holes spaced circumferentially aroundthe flange 30.1 and stationary carrier ring 28. Thus drive pins 31provide the necessary drive coupling between drive shaft 22 and carrierring 28 (via shaft sleeve 30). An O-ring 42 is provided between carrierring 28 and shaft sleeve 30 as a static seal between the two elements.Carrier ring 28 is held is position on shaft sleeve 30 by means of acirclip 28.1.

An adaptor ring 32 is further provided which is bolted to pump casing 21by means of bolts 33 and an adjustable cover ring 34 is mounted toadaptor ring 32 by means of three threaded shafts 35, nuts 36 and locknuts 37 as shown.

In use, biassing means 38 which is of the kind as shown in FIG. 1 islocated in a tensioned state between non-rotatable carrier ring 29 andcover ring 34 which forms part of the pump casing structure 20.1. Bothcarrier ring 29 and cover ring 34 feature recess formations 29.1 and34.1 respectively which are complementary to the outer diameter of thebiassing means 38 on either side thereof for static sealing engagementwith the biassing means. The biassing means 38 is thus anchored to thecarrier ring 29 and cover ring 34 by way of frictional abutment, andthis eliminates the necessity to provide mechanical anchoringarrangements such as drive pins, lugs etc.

An O-ring 39 is provided as a static seal between adaptor ring 32 andcover ring 34.

The entire seal ring assembly is in cartridge form and may be installedas a unit over drive shaft 22. Once installed, cover ring 34 issufficiently advanced in direction A to apply a pre-determinedcompression loading on biassing means 38 whereafter lock nuts 37 aretightened to retain cover ring 34 in position. As and when required, forexample when seal faces 25 and 27 have worn appreciably, cover ring 34may be advanced further to bring biassing means 38 to the requiredcompression loading. This may be done while the pump is in operation.

In use, the biassing means 38 urges non-rotatable seal ring 26 towardsrotating seal ring 24 (mechanical closing force) which effects sealingengagement of the seal faces 25 and 27. However, during normal operationof the pump, a thin film of fluid, (not shown), is present between sealfaces 25 and 27 which positively acts to urge the seal faces away fromeach other (hydraulic opening force). The presence of the fluid film isnecessary to provide lubrication and cooling to the seal faces, and anabsence of fluid between the seal faces will result in rapid failure ofthe seal due to friction and over-heating of the lapped seal faces 25and 27.

Furthermore, any hydraulic fluid pressure within the pump casing 21 willprovide an hyraulic closing force on surface 38.1 of biassing means 38.This hydraulic closing force will obviously be complementary to themechanical closing force. It would be undesireable if this hydraulicclosing force becomes excessive since it could cause the fluid film (notshown) to be expelled completely from between the seal faces 25 and 27,which will result in dry contact between the seal faces and consequentlyearly failure as outlined above. It is thus intended that the surfacearea 38.1 be pre-determined to allow the hydraulic closing force actingon that surface to be of the same magnitude as the hydraulic openingforce acting in the opposite direction between the seal faces 26 and 27.When this is achieved, the mechanical closing force applied by the discsprings represents the net closing force remaining after the hydraulicopening and closing forces have been balanced out.

In FIG. 3, seal ring 26 is bonded by way of vulcanizing directly to theelastomeric body of biasing means 38. This is achieved by moulding sealring 26 in place during the manufacturing process of biasing means 38.This variation dispenses with the necessity to provide a carrier ring 29(see FIG. 2).

Furthermore, in this embodiment, flange 30.1 is enlarged when comparedto flange 30.1 shown in the embodiment of FIG. 2. The carrier ring 28shown in FIG. 2 is replaced by an elastomeric collar 30.2 which isbonded by vulcanizing to seal ring 24 and flange 30.1 of shaft sleeve30. With this arrangement, the drive pins 31, O-ring 42 and circlip 28.1shown in the embodiment of FIG. 2 are all redundant.

Referring again to FIG. 2, a further requirement for proper operation ofthe mechanical seal is that the non-rotatable seal ring 26 must beaxially aligned with rotatable seal ring 24, and they must both beconcentric with drive shaft 22.

Concentricity and axial alignment of the seal faces may be achieved bymeans of a threaded plastic setting collar 40 which fits, in use, in theannular space 40.1 defined between the inner diameter of cover ring 34and the outer diameter of shaft sleeve 30. Setting collar 40, whichfeatures a threaded bore 40.1, is advanced axially along a threadedportion of shaft sleeve 30. In use, setting collar 40 is fully advanceduntil it abuts against the complementary recess 34.2 along the innerdiameter of cover ring 34 as shown. When in this position, thesub-assembly comprising the shaft sleeve 30, carrier ring 29, biassingmeans 38, cover ring 34, adaptor ring 32 and setting collar 40 is incartridge form, and may be removed from the end of drive shaft 22 forpurposes of maintainance, and a new or repaired sub-assembly may befitted to the shaft 22 in cartridge form.

In practise, the sub-assembly as described above is pre-assembled on awork bench. The collar 40 is advanced until it abuts against recess 34.2of cover ring 34. A further slight compression pre-loading ofapproximately one quarter turn is applied purely nominally to load theseal faces 25 and 27 by compressing the biassing means 38. The collar 40will be secure in this position due to the pre-loading force applied onit by the biassing means 38. The adaptor ring 32 is retracted as far asit will go towards cover ring 34 and retained in that position byadjusting nuts 37 and 36. At this point, the assembly is in cartridgeform and is ready to be mounted over the end of drive shaft 22.

The pump casing 21 and impeller 23 is mounted to the end of drive shaft22 in the conventional manner once the sub-assembly is in place.

The cartridge sub-assembly, once mounted to shaft 22, is not toucheduntil the pump casing 21 is completely fitted and all pipework andfastenings (not shown) completed. Once this has been completed, adaptorring 32 is advanced to pump casing 21 (by adjusting nuts 36 and 37) andfastened thereto by way of bolts 33.

Nuts 36 are next advanced against cover ring 34 to effect the desiredfinal compression loading on the seal faces 25 and 27. Lock nuts 37 aretightened against cover ring 34 to lock the cover ring 34 in the desiredposition.

Once this has been done, collar 40 is retracted from under cover ring 34and cap screw 41 may be tightened on a non-threaded portion (not shown)of shaft sleeve 30 to keep it clear from cover ring 34 during normaloperation of the pump. By this method non-rotatable seal ring 24 isperfectly aligned with rotatable seal ring 24 and is furthermoreconcentric with drive shaft 22 regardless of any misalignments or out ofsquareness of pump casing 21 with respect to shaft 22.

It will be appreciated that many modifications or variations of theinvention are possible without departing from the scope of the appendedclaims.

I claim:
 1. A mechanical seal arrangement for use in association with apump casing structure and a drive shaft for driving a pump impellerwhich is housed in the pump casing structure, the seal arrangementcomprising:a rotatable seal ring having a seal face mountableconcentrically on the drive shaft for rotation with the drive shaft; anon-rotatable seal ring having a seal face mountable in axial alignementwith the rotatable seal ring; and biasing means for providing a biasingforce to urge the rotatable and non-rotatable seal rings axially towardseach other for effecting sealing engagement of the seal faces thereof;the arrangement being characterized by the biasing means comprising atleast two disk spring elements spaced apart and encapsulated in anelastomeric body, which defines in use a pressure surface against whicha fluid may exert a force complementary to the biasing force of thebiasing means, the biasing means being locatable in a tensioned statebetween either one of the seal rings and the pump casing structure; andby the non-rotatable seal ring being bonded directly to the elastomericbody of the biasing means, with the rotatable seal ring being bondeddirectly to a shaft sleeve fitted over the drive shaft.
 2. A mechanicalseal arrangement as claimed in claim 1 including a first carrier ring towhich the non-rotatable seal ring is mounted; the pump casing structurefurther including a pump casing and a cover ring which is mountable tothe pump casing, the arrangement being characterized therein that inuse, the biasssing means is located in a tensioned state between thefirst carrier ring and the cover ring.
 3. A mechanical seal arrangementas claimed in claim 2 wherein the cover ring is adjustable relative tothe pump casing for adjusting the biassing force of the biassing means.4. A mechanical seal arrangement as claimed in claim 2 wherein anannular space is defined between the inner diameter of the cover ringand the outer diameter of the shaft sleeve, a setting collar beinglocatable in the annular space for locating the cover ringconcentrically relative to the drive shaft.
 5. A mechanical sealarrangement as claimed in claim 4 wherein the setting collar isremovably attachable to the shaft sleeve.
 6. A mechanical sealarrangement as claimed in claim 5 wherein the pump casing structurefurther includes an adaptor ring, and wherein the shaft sleeve; thesecond carrier ring with the rotatable seal ring; the first carrier ringwith the non-rotatable seal ring; the cover ring; the adaptor ring andthe setting collar are removable from the drive shaft as a unit incartridge form.